US20070292264A1 - Turbomachine stator including a stage of stator vanes actuated by an automatically centered rotary ring - Google Patents
Turbomachine stator including a stage of stator vanes actuated by an automatically centered rotary ring Download PDFInfo
- Publication number
- US20070292264A1 US20070292264A1 US11/763,181 US76318107A US2007292264A1 US 20070292264 A1 US20070292264 A1 US 20070292264A1 US 76318107 A US76318107 A US 76318107A US 2007292264 A1 US2007292264 A1 US 2007292264A1
- Authority
- US
- United States
- Prior art keywords
- ring
- wheels
- pin
- casing
- stator according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/162—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for axial flow, i.e. the vanes turning around axes which are essentially perpendicular to the rotor centre line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
- F02C9/16—Control of working fluid flow
- F02C9/20—Control of working fluid flow by throttling; by adjusting vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/50—Kinematic linkage, i.e. transmission of position
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T50/00—Aeronautics or air transport
- Y02T50/60—Efficient propulsion technologies, e.g. for aircraft
Definitions
- the invention relates to a turbomachine stator.
- the invention applies to terrestrial or aviation turbomachines, in particular to airplane turbojets, and more particularly to the compressors included in such turbomachines.
- the invention relates to a turbomachine of the type comprising a stator having a casing and at least one stage of variable-pitch stator vanes, said vanes being moved by an actuator ring outside said casing and carried thereby, said ring being coupled by links to said vanes of said stage in order to actuate them simultaneously.
- the stator of the compressor is fitted with at least one stage of stator vanes that are said to be of variable pitch since their position in the stream is adjustable. More precisely, the angle of attack of the vanes can be controlled as a function of the operating conditions of the turbomachine by a servo-control system that controls displacement of a rotary actuator ring outside the casing and connected to said vanes by respective links.
- such an actuator ring has radially-adjustable centering shoes enabling it to be positioned around the casing by pressing thereagainst.
- Each centering shoe bears against a track on the casing, i.e. on a projection defined on the surface thereof, the projections being machined so that their contact surfaces are inscribed on a cylindrical surface of axis that coincides with the axis of the turbomachine.
- U.S. Pat. No. 4,130,375 describes an actuator ring that moves circularly only, and that is made up of two superposed rings.
- the inner ring is mounted on the casing by means of studs projecting radially, and the outer ring that is attached to the vane actuator links runs on the inner ring via wheels.
- Such a system is heavy and bulky.
- the invention provides a noticeable improvement in comparison with the above-mentioned prior art solutions, and, in operation, it enables the ring to be centered automatically while using a system that is relatively compact.
- the invention relates to a turbomachine stator of the above-mentioned type, wherein said casing includes a stationary coaxial rail projecting from the outside surface of the casing, wherein at least three circumferentially spaced-apart groups of wheels are constrained to move along said rail, wherein each group of wheels is coupled to said ring by a radial guidance arrangement (i.e. each group of wheels is guided radially relative to the ring), and wherein each group of wheels comprises at least two wheels engaged with said rail, each wheel being mounted to rotate on a radially-oriented pin, said pin being mounted directly on said ring.
- each wheel slides radially along its pin, and the pin is stationary relative to the ring.
- the pin may be mounted in stationary manner to the ring or it may be formed integrally therewith.
- each wheel is secured to its pin and the pin is mounted slidably in a bore formed in the ring, such that the wheel and the pin slide radially together relative to the ring.
- the pin is movable in radial translation relative to the ring, while the wheel is movable relative to the pin only in rotation (and not in translation).
- a smooth bearing or a rolling bearing is provided between the bore and the pin.
- the structure in accordance with the invention makes it possible to obtain an actuator ring of low weight, and that is accurately centered (i.e. coaxial about the casing).
- assembly and adjustment of such a structure are simple and can be performed quickly.
- the structure in accordance with the invention guarantees that the initial quality of centering is permanent, regardless of the operating temperature and regardless of the materials used for the ring and the casing. This improves control over the position of the actuator ring during all stages of control.
- the system proposed can be satisfied with three (the minimum number) or four groups of wheels that are substantially equidistant from one another, circumferentially.
- the actuator ring In order to turn the actuator ring, it is generally driven by control actuators, located at one or two points of its periphery.
- control actuators located at one or two points of its periphery.
- the drive forces needed are reduced by the amount needed in the prior art in order to overcome friction between the centering shoes and the projections, this amount constituting about 30% of the total drive force needed.
- the resulting saving can have repercussions on the size of the control actuator(s) or of any other control device.
- said rail is made up of two parallel rings secured to the casing, and said at least two wheels in each group of wheels come respectively into contact with the two rings.
- Each group of wheels generally comprises more than two wheels, and the wheels are distributed as equally as possible between the rings.
- the two rings are provided with facing lateral ribs and the groups of wheels comprise wheels, e.g. in the form of double cones, that are in engagement with said lateral ribs.
- said rail is constituted by a single ring secured to said casing, and the wheels in each group of wheels come into contact with said ring, on either side thereof.
- the actuator ring in order to turn the actuator ring, it is generally driven from one or two points of its periphery. Pivoting the variable-pitch vanes in their housings takes place with friction that can oppose such movement. This opposition has repercussions on the links, and in some cases can lead to elliptical deformation of the ring which is accompanied by (small) misalignment of the axes relative to the radial direction.
- the invention also provides a turbomachine provided with such a stator, in particular the invention provides a compressor with such a stator.
- FIG. 1 is a view on a section of casing, perpendicular to the axis of the turbomachine, showing how an actuator ring is mounted around said casing;
- FIG. 2 is a side view in perspective showing a portion of the ring and of the casing of FIG. 1 ;
- FIG. 3 is a plan view in perspective of a portion of the ring and the casing of FIG. 1 ;
- FIG. 4 is a plan view (looking from outside the ring towards the inside) showing a portion of the ring and of the casing of FIG. 1 ;
- FIG. 5 is a view from beneath (from the inside of the ring looking towards the outside) showing a portion of the ring and of the casing of FIG. 1 .
- FIGS. 1 and 2 show a portion of a turbomachine casing 11 of axis X and housing variable pitch stator vanes 12 .
- Each vane 12 has a pivot 14 projecting from the casing 11 and connected via a link 16 to an actuator ring 18 on the outside of the casing.
- the ring 18 presents tenons 21 secured to the ends of the links 16 . It can be understood that turning the actuator ring about the axis X causes the vanes 12 to pivot simultaneously through the same angle. In an airplane turbojet, the orientation of the vanes can be adjusted as a function of flying conditions.
- the invention makes it possible to guarantee that the actuator ring 18 is centered, with said centering not being disturbed by differences in expansion between the casing 11 and the ring 18 .
- the casing 11 has on its outside a stationary coaxial annular rail 24 , in this case formed integrally with the wall of the casing and projecting from its outside surface.
- At least three groups of circumferentially spaced-apart wheels 26 that are preferably substantially equidistant from one another are constrained to move along the rail 24 .
- the rail is embodied completely only over those segments where it is functionally useful, i.e. along the paths followed by the groups of wheels 26 (see FIG. 1 ).
- the rail is omitted over other segments, thereby achieving a significant saving in weight and making it easier to put the groups of wheels into place.
- each group of wheels 26 is coupled to the ring 18 by a radial guide arrangement (i.e.
- each group of wheels is guided radially relative to the ring) that automatically ensures accurate centering of the ring 18 relative to the axis X of the turbomachine.
- four groups of wheels 26 are provided that are regularly spaced at 90° intervals relative to one another.
- the ring 18 is made up of an assembly of a plurality of curved segments 38 , 39 having flats at their ends and interconnected end to end, e.g. by crimping or by bolting so as to build up an annular structure (see FIG. 1 ).
- the segments 38 are those that carry the groups of wheels 26 .
- the rail 24 is made up of two parallel rings 30 a , 30 b (in fact ring segments) that are secured to the casing, and the groups of wheels 26 are shaped so as to move between these rings, more precisely between these ring segments.
- the two rings 30 a , 30 b are provided with lateral ribs 32 a , 32 b that face each other, and the groups of wheels 26 include double-cone wheels 34 that are in rolling engagement with the lateral ribs.
- each group of wheels 26 comprises three double-cone wheels 34 , each wheel being mounted to rotate about a pin 36 .
- the three wheels together form an isosceles triangle.
- One of the wheels 34 engages with one of the rings 30 a
- the other two wheels 34 engage with the other ring 30 b .
- a bearing system is interposed between each wheel 34 and its pin 36 .
- the wheels 34 cannot slide along the pins 36 .
- the pins 36 are integral with the ring 18 .
- the pins 36 are slidably mounted in bores 40 of complementary shape formed in the ring 18 . These bores 40 extend radially so that the pins 36 are oriented radially and slide radially relative to the ring 18 .
- a smooth bearing or a rolling bearing is provided between the pin and the bore.
- a bushing placed between the bore and the pin. It is also possible to use a coating deposited on the surface of the bore and/or on the surface of the pin. Naturally, the material of the bushing and/or of the coating is selected for its low coefficient of friction.
- the expansion of the casing is greater than the expansion of the ring 18 , so the diameter of the rings 30 a and 30 b increases faster than that of the ring 18 .
- the rings 30 a and 30 b take with them the wheels 34 and the pins 36 that then slide inside the bores 40 in an outward direction relative to the ring.
- the ring 18 which was centered before expansion continues to be centered after expansion.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
- The invention relates to a turbomachine stator.
- The invention applies to terrestrial or aviation turbomachines, in particular to airplane turbojets, and more particularly to the compressors included in such turbomachines.
- More precisely, the invention relates to a turbomachine of the type comprising a stator having a casing and at least one stage of variable-pitch stator vanes, said vanes being moved by an actuator ring outside said casing and carried thereby, said ring being coupled by links to said vanes of said stage in order to actuate them simultaneously.
- In a turbomachine of this type, the stator of the compressor is fitted with at least one stage of stator vanes that are said to be of variable pitch since their position in the stream is adjustable. More precisely, the angle of attack of the vanes can be controlled as a function of the operating conditions of the turbomachine by a servo-control system that controls displacement of a rotary actuator ring outside the casing and connected to said vanes by respective links.
- Conventionally, such an actuator ring has radially-adjustable centering shoes enabling it to be positioned around the casing by pressing thereagainst. Each centering shoe bears against a track on the casing, i.e. on a projection defined on the surface thereof, the projections being machined so that their contact surfaces are inscribed on a cylindrical surface of axis that coincides with the axis of the turbomachine.
- The adjustments of the shoes enabling the ring to be made suitably coaxial with the casing are difficult to make and take time. In addition, once such adjustments have been made, it is necessary to give the sliding assembly a certain amount of clearance between the shoes and the projections in order to accommodate expansion phenomena that occur in operation and that involve dimensions varying differently for the ring and the casing. The ring and the casing have different coefficients of expansion, and in addition they are exposed to different operating temperatures. This operating clearance that is required can be as great as 0.7 millimeters (mm) to 0.8 mm, which goes against achieving the desired centering. When cold, this operating clearance is at a maximum, so the off-center position of the ring is therefore at its maximum.
- In another design, U.S. Pat. No. 4,130,375 describes an actuator ring that moves circularly only, and that is made up of two superposed rings. The inner ring is mounted on the casing by means of studs projecting radially, and the outer ring that is attached to the vane actuator links runs on the inner ring via wheels. Such a system is heavy and bulky.
- The invention provides a noticeable improvement in comparison with the above-mentioned prior art solutions, and, in operation, it enables the ring to be centered automatically while using a system that is relatively compact.
- More precisely, the invention relates to a turbomachine stator of the above-mentioned type, wherein said casing includes a stationary coaxial rail projecting from the outside surface of the casing, wherein at least three circumferentially spaced-apart groups of wheels are constrained to move along said rail, wherein each group of wheels is coupled to said ring by a radial guidance arrangement (i.e. each group of wheels is guided radially relative to the ring), and wherein each group of wheels comprises at least two wheels engaged with said rail, each wheel being mounted to rotate on a radially-oriented pin, said pin being mounted directly on said ring.
- The fact that the pin is mounted directly on the ring means that the pin is not mounted on a support that is in turn mounted to the ring. Two configurations can thus be envisaged.
- In a first configuration, each wheel slides radially along its pin, and the pin is stationary relative to the ring. The pin may be mounted in stationary manner to the ring or it may be formed integrally therewith.
- In a second configuration, each wheel is secured to its pin and the pin is mounted slidably in a bore formed in the ring, such that the wheel and the pin slide radially together relative to the ring. In other words, the pin is movable in radial translation relative to the ring, while the wheel is movable relative to the pin only in rotation (and not in translation).
- Advantageously, in order to facilitate sliding of the pin in the bore, a smooth bearing or a rolling bearing is provided between the bore and the pin.
- The structure in accordance with the invention makes it possible to obtain an actuator ring of low weight, and that is accurately centered (i.e. coaxial about the casing). In addition, assembly and adjustment of such a structure are simple and can be performed quickly. Finally, there is no need to provide operating clearance to accommodate expansion phenomena, thereby ensuring that the ring is properly centered regardless of the operating temperature, and in particular when cold.
- The structure in accordance with the invention guarantees that the initial quality of centering is permanent, regardless of the operating temperature and regardless of the materials used for the ring and the casing. This improves control over the position of the actuator ring during all stages of control.
- The system proposed can be satisfied with three (the minimum number) or four groups of wheels that are substantially equidistant from one another, circumferentially.
- In order to turn the actuator ring, it is generally driven by control actuators, located at one or two points of its periphery. By means of the invention the drive forces needed are reduced by the amount needed in the prior art in order to overcome friction between the centering shoes and the projections, this amount constituting about 30% of the total drive force needed. The resulting saving can have repercussions on the size of the control actuator(s) or of any other control device.
- Compared with the system described in above-mentioned U.S. Pat. No. 4,130,375, it can be seen that the weight and the dimensions of the actuator ring are greatly reduced since the inner ring of the system described in that patent is omitted.
- In a possible variant, said rail is made up of two parallel rings secured to the casing, and said at least two wheels in each group of wheels come respectively into contact with the two rings. Each group of wheels generally comprises more than two wheels, and the wheels are distributed as equally as possible between the rings.
- For example, the two rings are provided with facing lateral ribs and the groups of wheels comprise wheels, e.g. in the form of double cones, that are in engagement with said lateral ribs.
- In another variant, said rail is constituted by a single ring secured to said casing, and the wheels in each group of wheels come into contact with said ring, on either side thereof.
- As mentioned above, in order to turn the actuator ring, it is generally driven from one or two points of its periphery. Pivoting the variable-pitch vanes in their housings takes place with friction that can oppose such movement. This opposition has repercussions on the links, and in some cases can lead to elliptical deformation of the ring which is accompanied by (small) misalignment of the axes relative to the radial direction. To solve this additional problem, it is possible to act on the section of the ring so as to make it stiffer (improve resistance to deformation) and/or to act on the nature of the material constituting said ring, preferring to use materials presenting high stiffness. This applies in particular to certain composite materials based on carbon fibers.
- The invention also provides a turbomachine provided with such a stator, in particular the invention provides a compressor with such a stator.
- The invention can be better understood and other advantages thereof appear more clearly in the light of the following description of an embodiment of the invention. The description is made with reference to the accompanying sheets of figures, in which:
-
FIG. 1 is a view on a section of casing, perpendicular to the axis of the turbomachine, showing how an actuator ring is mounted around said casing; -
FIG. 2 is a side view in perspective showing a portion of the ring and of the casing ofFIG. 1 ; -
FIG. 3 is a plan view in perspective of a portion of the ring and the casing ofFIG. 1 ; -
FIG. 4 is a plan view (looking from outside the ring towards the inside) showing a portion of the ring and of the casing ofFIG. 1 ; and -
FIG. 5 is a view from beneath (from the inside of the ring looking towards the outside) showing a portion of the ring and of the casing ofFIG. 1 . -
FIGS. 1 and 2 show a portion of aturbomachine casing 11 of axis X and housing variablepitch stator vanes 12. Eachvane 12 has apivot 14 projecting from thecasing 11 and connected via alink 16 to anactuator ring 18 on the outside of the casing. On its outside surface, thering 18 presentstenons 21 secured to the ends of thelinks 16. It can be understood that turning the actuator ring about the axis X causes thevanes 12 to pivot simultaneously through the same angle. In an airplane turbojet, the orientation of the vanes can be adjusted as a function of flying conditions. - The invention makes it possible to guarantee that the
actuator ring 18 is centered, with said centering not being disturbed by differences in expansion between thecasing 11 and thering 18. - To do this, the
casing 11 has on its outside a stationary coaxialannular rail 24, in this case formed integrally with the wall of the casing and projecting from its outside surface. At least three groups of circumferentially spaced-apart wheels 26 that are preferably substantially equidistant from one another are constrained to move along therail 24. The rail is embodied completely only over those segments where it is functionally useful, i.e. along the paths followed by the groups of wheels 26 (seeFIG. 1 ). The rail is omitted over other segments, thereby achieving a significant saving in weight and making it easier to put the groups of wheels into place. In addition, and as explained below, each group ofwheels 26 is coupled to thering 18 by a radial guide arrangement (i.e. each group of wheels is guided radially relative to the ring) that automatically ensures accurate centering of thering 18 relative to the axis X of the turbomachine. In the example, four groups ofwheels 26 are provided that are regularly spaced at 90° intervals relative to one another. - In the example of the figures, the
ring 18 is made up of an assembly of a plurality ofcurved segments FIG. 1 ). Thesegments 38 are those that carry the groups ofwheels 26. - In the example being described, the
rail 24 is made up of twoparallel rings wheels 26 are shaped so as to move between these rings, more precisely between these ring segments. In addition, the tworings lateral ribs wheels 26 include double-cone wheels 34 that are in rolling engagement with the lateral ribs. - In the example shown, each group of
wheels 26 comprises three double-cone wheels 34, each wheel being mounted to rotate about apin 36. The three wheels together form an isosceles triangle. One of thewheels 34 engages with one of therings 30 a, while the other twowheels 34 engage with theother ring 30 b. In order to enable the wheels to turn, a bearing system is interposed between eachwheel 34 and itspin 36. Thewheels 34 cannot slide along thepins 36. - In another embodiment (not shown), the
pins 36 are integral with thering 18. - In the example shown, the
pins 36 are slidably mounted inbores 40 of complementary shape formed in thering 18. These bores 40 extend radially so that thepins 36 are oriented radially and slide radially relative to thering 18. - In order to make it easier for each
pin 36 to slide in itsbore 40, a smooth bearing or a rolling bearing is provided between the pin and the bore. - For a rolling bearing, it is advantageous to use a ring with recirculating balls. It would also be possible to use a ball cage mounted on a damper system allowing the ball cage to move radially.
- For a smooth bearing, it is advantageous to use a bushing placed between the bore and the pin. It is also possible to use a coating deposited on the surface of the bore and/or on the surface of the pin. Naturally, the material of the bushing and/or of the coating is selected for its low coefficient of friction.
- In general, when the temperature rises in operation, the expansion of the casing is greater than the expansion of the
ring 18, so the diameter of therings ring 18. By means of the invention, therings wheels 34 and thepins 36 that then slide inside thebores 40 in an outward direction relative to the ring. Thus, thering 18 which was centered before expansion continues to be centered after expansion.
Claims (12)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0652528A FR2902454A1 (en) | 2006-06-16 | 2006-06-16 | TURBOMACHINE STATOR COMPRISING A FLOOR OF ADJUSTERS ADJUSTED BY A ROTATING CROWN WITH AUTOMATIC CENTERING |
FR0652528 | 2006-06-16 |
Publications (2)
Publication Number | Publication Date |
---|---|
US20070292264A1 true US20070292264A1 (en) | 2007-12-20 |
US7938620B2 US7938620B2 (en) | 2011-05-10 |
Family
ID=37734946
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/763,181 Active 2030-02-09 US7938620B2 (en) | 2006-06-16 | 2007-06-14 | Turbomachine stator including a stage of stator vanes actuated by an automatically centered rotary ring |
Country Status (7)
Country | Link |
---|---|
US (1) | US7938620B2 (en) |
EP (1) | EP1867841B1 (en) |
JP (1) | JP5220351B2 (en) |
CA (1) | CA2591770C (en) |
DE (1) | DE602007005543D1 (en) |
FR (1) | FR2902454A1 (en) |
RU (1) | RU2454548C2 (en) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2211026A2 (en) * | 2009-01-26 | 2010-07-28 | Rolls-Royce plc | A variable stator vane assembly in a gas turbine engine |
CN102619736A (en) * | 2012-04-16 | 2012-08-01 | 杭州杭氧透平机械有限公司 | Executive mechanism of air-intake-adjustable flow guide cascade of oxygen compressor |
US20140110554A1 (en) * | 2011-06-07 | 2014-04-24 | Toyota Shatai Kabushiki Kaisha | Seat sliding device |
WO2014070630A1 (en) * | 2012-11-05 | 2014-05-08 | United Technologies Corporation | Gas turbine engine synchronization ring |
EP2752583A1 (en) * | 2011-11-02 | 2014-07-09 | Mitsubishi Heavy Industries, Ltd. | Axial-flow fluid machine, and variable stationary-blade driving device therefor |
WO2014200680A1 (en) * | 2013-06-14 | 2014-12-18 | United Technologies Corporation | Radial fastening of tubular synchronizing rings |
US20170211410A1 (en) * | 2016-01-22 | 2017-07-27 | United Technologies Corporation | Variable vane stabilizer |
US20180328219A1 (en) * | 2015-11-04 | 2018-11-15 | Kawasaki Jukogyo Kabushiki Kaisha | Variable stator blade operating device |
CN109372592A (en) * | 2018-11-27 | 2019-02-22 | 中国航发沈阳发动机研究所 | A kind of regulating mechanism with displacement coordination ability |
US11840959B2 (en) | 2020-03-31 | 2023-12-12 | Kawasaki Jukogyo Kabushiki Kaisha | Unison ring of gas turbine engine |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9284851B2 (en) * | 2012-02-21 | 2016-03-15 | Mitsubishi Heavy Industries, Ltd. | Axial-flow fluid machine, and variable vane drive device thereof |
US20140314549A1 (en) * | 2013-04-17 | 2014-10-23 | General Electric Company | Flow manipulating arrangement for a turbine exhaust diffuser |
US9644491B2 (en) | 2014-06-13 | 2017-05-09 | Pratt & Whitney Canada Corp. | Single bolting flange arrangement for variable guide vane connection |
FR3041714B1 (en) * | 2015-09-30 | 2020-02-14 | Safran Aircraft Engines | TURBOMACHINE COMPRESSOR, ESPECIALLY AN AIRPLANE TURBOPROPELLER OR TURBOREACTOR |
FR3054006B1 (en) | 2016-07-12 | 2020-05-08 | Safran Aircraft Engines | ASSEMBLY FOR THE CONTROL OF VARIABLE TIMING BLADES IN A TURBOMACHINE |
US10502091B2 (en) * | 2016-12-12 | 2019-12-10 | United Technologies Corporation | Sync ring assembly and associated clevis including a rib |
FR3063779B1 (en) * | 2017-03-07 | 2022-11-04 | Safran Aircraft Engines | STATOR BLADE STAGE TIMING CONTROL RING |
US10526911B2 (en) | 2017-06-22 | 2020-01-07 | United Technologies Corporation | Split synchronization ring for variable vane assembly |
CN108167031A (en) * | 2018-03-06 | 2018-06-15 | 哈尔滨广瀚燃气轮机有限公司 | A kind of gas turbine adjustable guide vane executing agency |
FR3082562B1 (en) * | 2018-06-19 | 2020-06-12 | Safran Aircraft Engines | DISCHARGE DOOR CONTROL RING FOR AN AIRCRAFT TURBOMACHINE AND TURBOMACHINE COMPRISING SAME |
CN113623271A (en) * | 2020-05-06 | 2021-11-09 | 中国航发商用航空发动机有限责任公司 | Gas turbine, adjustable guide vane adjusting mechanism and linkage ring limiting device thereof |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3841788A (en) * | 1972-10-28 | 1974-10-15 | J Sljusarev | Device for turning the stator vanes of turbo-machines |
US3990809A (en) * | 1975-07-24 | 1976-11-09 | United Technologies Corporation | High ratio actuation linkage |
US4035101A (en) * | 1976-03-24 | 1977-07-12 | Westinghouse Electric Corporation | Gas turbine nozzle vane adjusting mechanism |
US4773821A (en) * | 1986-12-17 | 1988-09-27 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation "S.N.E.C.M.A." | Control mechanism for variably settable vanes of a flow straightener in a turbine plant |
US4810165A (en) * | 1986-07-09 | 1989-03-07 | Mtu Motoren- Und Turbinen-Union Munchen Gmbh | Adjusting mechanism for guide blades of turbo-propulsion units |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE496713A (en) * | 1949-07-01 | |||
US2933234A (en) * | 1954-12-28 | 1960-04-19 | Gen Electric | Compressor stator assembly |
US3685920A (en) * | 1971-02-01 | 1972-08-22 | Gen Electric | Actuation ring for variable geometry compressors or gas turbine engines |
CA1034509A (en) * | 1975-10-14 | 1978-07-11 | John Korta | Vane rotator assembly for a gas turbine |
JPS6121840U (en) * | 1984-07-13 | 1986-02-08 | トヨタ自動車株式会社 | Support structure of link drive ring for variable nozzle of gas turbine engine |
GB2206381B (en) * | 1987-06-30 | 1991-10-09 | Rolls Royce Plc | A variable stator vane arrangement for a compressor |
US4925364A (en) * | 1988-12-21 | 1990-05-15 | United Technologies Corporation | Adjustable spacer |
DE4102188C2 (en) * | 1991-01-25 | 1994-09-22 | Mtu Muenchen Gmbh | Guide vane adjustment device of a turbine of a gas turbine engine |
US5993152A (en) * | 1997-10-14 | 1999-11-30 | General Electric Company | Nonlinear vane actuation |
FR2879687B1 (en) * | 2004-12-16 | 2007-04-20 | Snecma Moteurs Sa | STATOR TURBOMACHINE COMPRISING A RECTIFIER AUBES STAGE ACTED BY A ROTATING CROWN DISPLACED BY ELECTRIC MOTOR MEANS |
FR2879686B1 (en) * | 2004-12-16 | 2007-04-06 | Snecma Moteurs Sa | STATOR TURBOMACHINE COMPRISING A RECTIFIER AUBES STAGE ACTED BY A ROTATING CROWN WITH AUTOMATIC CENTERING |
-
2006
- 2006-06-16 FR FR0652528A patent/FR2902454A1/en not_active Withdrawn
-
2007
- 2007-06-14 DE DE602007005543T patent/DE602007005543D1/en active Active
- 2007-06-14 US US11/763,181 patent/US7938620B2/en active Active
- 2007-06-14 EP EP07110288A patent/EP1867841B1/en active Active
- 2007-06-15 RU RU2007122467/06A patent/RU2454548C2/en active
- 2007-06-15 JP JP2007158244A patent/JP5220351B2/en active Active
- 2007-06-15 CA CA2591770A patent/CA2591770C/en active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3841788A (en) * | 1972-10-28 | 1974-10-15 | J Sljusarev | Device for turning the stator vanes of turbo-machines |
US3990809A (en) * | 1975-07-24 | 1976-11-09 | United Technologies Corporation | High ratio actuation linkage |
US4035101A (en) * | 1976-03-24 | 1977-07-12 | Westinghouse Electric Corporation | Gas turbine nozzle vane adjusting mechanism |
US4810165A (en) * | 1986-07-09 | 1989-03-07 | Mtu Motoren- Und Turbinen-Union Munchen Gmbh | Adjusting mechanism for guide blades of turbo-propulsion units |
US4773821A (en) * | 1986-12-17 | 1988-09-27 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation "S.N.E.C.M.A." | Control mechanism for variably settable vanes of a flow straightener in a turbine plant |
Cited By (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2211026A3 (en) * | 2009-01-26 | 2012-10-03 | Rolls-Royce plc | A variable stator vane assembly in a gas turbine engine |
EP2211026A2 (en) * | 2009-01-26 | 2010-07-28 | Rolls-Royce plc | A variable stator vane assembly in a gas turbine engine |
US20140110554A1 (en) * | 2011-06-07 | 2014-04-24 | Toyota Shatai Kabushiki Kaisha | Seat sliding device |
EP2752583A4 (en) * | 2011-11-02 | 2015-04-01 | Axial-flow fluid machine, and variable stationary-blade driving device therefor | |
EP2752583A1 (en) * | 2011-11-02 | 2014-07-09 | Mitsubishi Heavy Industries, Ltd. | Axial-flow fluid machine, and variable stationary-blade driving device therefor |
US9309897B2 (en) | 2011-11-02 | 2016-04-12 | Mitsubishi Hitachi Power Systems, Ltd. | Axial-flow fluid machinery, and variable vane drive device thereof |
CN102619736A (en) * | 2012-04-16 | 2012-08-01 | 杭州杭氧透平机械有限公司 | Executive mechanism of air-intake-adjustable flow guide cascade of oxygen compressor |
WO2014070630A1 (en) * | 2012-11-05 | 2014-05-08 | United Technologies Corporation | Gas turbine engine synchronization ring |
US9422825B2 (en) | 2012-11-05 | 2016-08-23 | United Technologies Corporation | Gas turbine engine synchronization ring |
WO2014200680A1 (en) * | 2013-06-14 | 2014-12-18 | United Technologies Corporation | Radial fastening of tubular synchronizing rings |
US10161407B2 (en) | 2013-06-14 | 2018-12-25 | United Technologies Corporation | Radial fastening of tubular synchronizing rings |
US20180328219A1 (en) * | 2015-11-04 | 2018-11-15 | Kawasaki Jukogyo Kabushiki Kaisha | Variable stator blade operating device |
US10669882B2 (en) * | 2015-11-04 | 2020-06-02 | Kawasaki Jukogyo Kabushiki Kaisha | Variable stator blade operating device |
US20170211410A1 (en) * | 2016-01-22 | 2017-07-27 | United Technologies Corporation | Variable vane stabilizer |
US10352186B2 (en) * | 2016-01-22 | 2019-07-16 | United Technologies Corporation | Variable vane stabilizer |
US11008886B2 (en) | 2016-01-22 | 2021-05-18 | Raytheon Technologies Corporation | Variable vane stabilizer |
CN109372592A (en) * | 2018-11-27 | 2019-02-22 | 中国航发沈阳发动机研究所 | A kind of regulating mechanism with displacement coordination ability |
US11840959B2 (en) | 2020-03-31 | 2023-12-12 | Kawasaki Jukogyo Kabushiki Kaisha | Unison ring of gas turbine engine |
Also Published As
Publication number | Publication date |
---|---|
CA2591770A1 (en) | 2007-12-16 |
DE602007005543D1 (en) | 2010-05-12 |
EP1867841A1 (en) | 2007-12-19 |
RU2454548C2 (en) | 2012-06-27 |
JP5220351B2 (en) | 2013-06-26 |
CA2591770C (en) | 2014-06-03 |
EP1867841B1 (en) | 2010-03-31 |
FR2902454A1 (en) | 2007-12-21 |
RU2007122467A (en) | 2008-12-20 |
US7938620B2 (en) | 2011-05-10 |
JP2007332970A (en) | 2007-12-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7938620B2 (en) | Turbomachine stator including a stage of stator vanes actuated by an automatically centered rotary ring | |
US11022145B2 (en) | Bushing arranged between a body and a shaft, and connected to the shaft | |
USRE42523E1 (en) | Stator vane stage actuated by an automatically-centering rotary actuator ring | |
US4755104A (en) | Stator vane linkage | |
US2933234A (en) | Compressor stator assembly | |
US8147187B2 (en) | Control of variable-pitch blades | |
CN107835889B (en) | Variable pitch blade control ring for a turbine | |
EP3244024B1 (en) | Mechanism and method for rapid response clearance control | |
US9353644B2 (en) | Synchronizing ring surge bumper | |
EP3290655B1 (en) | Variable stator vane setting | |
US5466122A (en) | Turbine engine stator with pivoting blades and control ring | |
US7845176B2 (en) | Mode strut and divergent flap interface | |
US10753231B2 (en) | Self-retaining bushing assembly | |
EP3336340B1 (en) | An actuation mechanism for a convergent/divergent gas turbine nozzle | |
EP3617461B1 (en) | Variable vane actuating system | |
US11111810B2 (en) | Control assembly for a stage of variable-pitch vanes for a turbine engine | |
RU2700113C2 (en) | Control system of blades with variable angle of installation for gas turbine engine | |
US6860717B2 (en) | Axial turbine for aeronautical applications | |
JP4615556B2 (en) | Fan nacelle for gas turbine engine, fan nacelle assembly, and method for changing annular fan outlet area of gas turbine engine | |
US10590957B2 (en) | Turbine engine compressor, in particular for an aircraft turboprop engine or turbojet engine | |
US10648359B2 (en) | System for controlling variable-setting blades for a turbine engine | |
US20200072074A1 (en) | Variable vane actuating system | |
GB2531922A (en) | System for controlling variable-pitch vanes for a turbine engine | |
RU2644001C2 (en) | Fan with variable angle of installation by various rotation of fan discs |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SNECMA, FRANCE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BOURU, MICHEL ANDRE;REEL/FRAME:019431/0089 Effective date: 20070412 |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
FPAY | Fee payment |
Year of fee payment: 4 |
|
AS | Assignment |
Owner name: SAFRAN AIRCRAFT ENGINES, FRANCE Free format text: CHANGE OF NAME;ASSIGNOR:SNECMA;REEL/FRAME:046479/0807 Effective date: 20160803 |
|
AS | Assignment |
Owner name: SAFRAN AIRCRAFT ENGINES, FRANCE Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE COVER SHEET TO REMOVE APPLICATION NOS. 10250419, 10786507, 10786409, 12416418, 12531115, 12996294, 12094637 12416422 PREVIOUSLY RECORDED ON REEL 046479 FRAME 0807. ASSIGNOR(S) HEREBY CONFIRMS THE CHANGE OF NAME;ASSIGNOR:SNECMA;REEL/FRAME:046939/0336 Effective date: 20160803 |
|
MAFP | Maintenance fee payment |
Free format text: PAYMENT OF MAINTENANCE FEE, 8TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1552); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 8 |
|
MAFP | Maintenance fee payment |
Free format text: PAYMENT OF MAINTENANCE FEE, 12TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1553); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 12 |